|Publication number||US8157543 B2|
|Application number||US 12/280,816|
|Publication date||Apr 17, 2012|
|Filing date||Jan 31, 2007|
|Priority date||Mar 23, 2006|
|Also published as||CN101405480A, CN101405480B, EP1998008A1, EP1998008A4, US20090056332, WO2007108234A1|
|Publication number||12280816, 280816, PCT/2007/51607, PCT/JP/2007/051607, PCT/JP/2007/51607, PCT/JP/7/051607, PCT/JP/7/51607, PCT/JP2007/051607, PCT/JP2007/51607, PCT/JP2007051607, PCT/JP200751607, PCT/JP7/051607, PCT/JP7/51607, PCT/JP7051607, PCT/JP751607, US 8157543 B2, US 8157543B2, US-B2-8157543, US8157543 B2, US8157543B2|
|Original Assignee||Ihi Corporation|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (132), Non-Patent Citations (29), Referenced by (2), Classifications (22), Legal Events (2)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This is a National Phase Application in the United States of International Patent Application No. PCT/JP2007/051607 filed Jan. 31, 2007, which claims priority on Japanese Patent Application No. 080527/2006, filed Mar. 23, 2006. The entire disclosures of the above patent applications are hereby incorporated by reference.
1. Field of the Invention
The present invention relates to a high-speed rotating shaft of a supercharger.
2. Description of Related Art
Previously compressing an air or an air-fuel mixture supplied to a cylinder of an internal combustion engine is called as a supercharging, and a compressor thereof is called as a supercharger. Further, a supercharger executing the supercharging by utilizing an exhaust gas of the engine is called as an exhaust gas turbine supercharger or a turbocharger for short. In the following description, in the present application, the turbocharger is simply called as “supercharger” except a particularly necessary case.
The bearing housing 3, the turbine housing 4, the compressor housing 5 a and the seal plate 5 b are coupled to each other in an illustrated order. Further, the turbine rotor shaft 1 is formed by integrating a turbine impeller 1 a and a rotor shaft 1 b in accordance with a welding or the like, is rotationally supported by a radial bearing within the bearing housing 3, and is coaxially coupled to the compressor impeller 2.
In accordance with this structure, it is possible to widely improve a performance of the internal combustion engine by rotationally driving the turbine impeller 1 a by the exhaust gas of the internal combustion engine, transmitting a rotating force to the compressor impeller 2 via the rotor shaft 1 b so as to rotationally drive the compressor impeller 2, and compressing the air (or the air-fuel mixture) so as to supply to the internal combustion engine.
In accordance with a high performance of the supercharger, the turbine rotor shaft 1 and the compressor impeller 2 are rotated at a high speed between several tens of thousand and several hundreds of thousand min-1. The floating metals 6 a and 6 b rotate at lower speed than the turbine rotor shaft because these metals are not fixed with the shaft, and the thrust collar 7 rotate at the same speed as that of the turbine rotor shaft because it is fixed with the shaft. Therefore the floating metals 6 a and 6 b and the thrust collar 7 support the radial force and the thrust force respectively while rotating with respective high speed. Further, in order to reduce a sliding resistance at a time of rotating, the structure is made such that a lubricating oil is always supplied to the sliding portion from an oil path 3 a provided in the bearing housing 3.
Further, as a bearing structure of the turbine rotor shaft rotating at a high speed, patent documents 1 to 3 have been already disclosed.
Patent Document 1: Japanese Unexamined Patent Publication No. 2000-110577 “bearing apparatus of supercharger”
Patent Document 2: Japanese Unexamined Patent Publication No. 2001-295655 “bearing apparatus of supercharger”
Patent Document 3: Japanese Unexamined Patent Publication No. 2005-23920 “bearing apparatus of supercharger”
As mentioned above, the high-speed rotating shaft (the turbine rotor shaft) of the conventional supercharger is normally supported by two radial bearings spaced at a fixed distance. In this case, a specific frequency ω of the high-speed rotating shaft can be expressed by an approximate expression (1) in the case of the high-speed rotating shaft except the turbine and the compressor in both ends.
In this case, reference symbol n(=1, 2, 3, . . .) denotes a vibration mode degree (primary, secondary and tertiary) of a both-end support shaft shown in
Further, if a diameter of the high-speed rotating shaft is set to d, an expression (2) can be obtained from the expression (1) on the basis of I=πd4/64, A=πd2/4, and (I/A)0.5=d/4.
In this case, each of the expressions mentioned above corresponds to the approximate expression, and it is practically necessary to determine a critical speed in accordance with a strict computer simulation or the like including the turbine and the compressor in both ends.
Hereinafter, the rotating speed corresponding to the primary, secondary and tertiary vibration modes is called as “critical speed of bending” or simply called as “critical speed”, in the present invention.
The high-speed rotating shaft of the conventional supercharger is designed such that the secondary critical speed of the shaft is sufficiently away from the rated speed which means maximum design speed. In such design, the primary critical speed becomes higher. Therefore when the rotating speed of the shaft passes through the primary critical speed, excitation energy applied to the supercharger becomes bigger and vibration and noise becomes larger.
Further, as shown in the drawing of the patent document 1, in order to improve a rotational stability of the supercharger, it is possible to decrease the primary critical speed of the high-speed rotating shaft by narrowing a distance between the bearings. Accordingly, for example, in the case that the rotating speed of the high-speed rotating shaft passes through the primary critical speed during the operation of the supercharger from a low-speed rotation to a high-speed rotation, there has been executed a reduction of a vibration and a noise by reducing an excitation energy applied to the supercharger.
However, as is apparent from the expression (2), it is generally possible to decrease the primary critical speed by narrowing a shaft diameter between the bearings, however, the secondary critical speed tends to be simultaneously decreased. Accordingly, there is a problem that the secondary critical speed is lowered largely in some shaft system so as to come close to the operation range and the shaft system becomes unstable.
The present invention is made for the purpose of simultaneously solving the problems mentioned above. In other words, an object of the present invention is to provide a high-speed rotating shaft of a supercharger which can decrease a primary critical speed while suppressing a decreasing of a secondary critical speed, with respect to a rated speed.
In accordance with the present invention, there is provided a high-speed rotating shaft of a supercharger which is rotatably supported by two radial bearings spaced at a fixed distance, directly couples a turbine impeller fixed to one end and a compressor impeller fixed to the other end, and transmits a rotational driving force of the turbine impeller to the compressor impeller, wherein a small shaft portion having a smaller diameter than a bearing portion is provided in an intermediate portion of the bearing, and the small shaft portion is offset in such a manner that a center of a distance between a starting point of the small shaft portion close to the turbine side and an end point close to the compressor side comes close to the compressor side with respect to a center between a distance between the two radial bearings.
In accordance with a preferable aspect of the present invention, an offset amount, a diameter and a length of the small shaft portion are set in accordance with a computer simulation in such a manner as to decrease a primary critical speed while suppressing a decreasing of a secondary critical speed with respect to a rated speed.
In accordance with the structure of the present invention, since the small shaft portion having the smaller diameter than the bearing portion is provided between the bearings of the high-speed rotating shaft, it is possible to decrease the primary critical speed of bending of the high-speed rotating shaft. Accordingly, in the case that the rotating speed of the high-speed rotating shaft passes through the primary critical speed during the operation of the supercharger, it is possible to reduce the vibration and the noise thereof.
Further, since the shaft diameter of the turbine side portion corresponding to a body portion of the secondary vibration mode of bending of the high-speed rotating shaft has approximately the same diameter as the bearing portion by offsetting the small shaft portion to the compressor side, a rigidity of the shaft positioned in the body portion of the secondary vibration mode of bending is not lowered. Therefore, it is possible to increase a stability of the shaft system and improve a reliability by suppressing the decreasing of the secondary critical speed of bending in such a manner that at least a decreasing amount of the secondary critical speed becomes smaller than a decreasing amount of the primary critical speed.
A description will be given below of a preferable embodiment in accordance with the present invention with reference to the accompanying drawings. In this case, the same reference numerals are attached to common portions in the respective drawings, and an overlapping description will be omitted.
In this case, in this drawing, the radial bearings 12 a and 12 b correspond to an integrally coupled journal bearing, however, the present invention is not limited to this, but the radial bearings may be independently provided as shown in
The high-speed rotating shaft 10 in accordance with the present invention is structured such that a turbine impeller 1 a is fixed to one end (a left end in the drawing) thereof, a compressor impeller 2 is fixed to the other end, the turbine impeller la is directly coupled to the compressor impeller 2, and a rotational driving force of the turbine impeller 1 a is transmitted to the compressor impeller 2.
The high-speed rotating shaft 10 in accordance with the present invention has a small shaft portion 14 having a diameter d smaller than a diameter D of the bearing portion between the bearings.
The high-speed rotating shaft 10 in accordance with the present invention corresponds to
The offset amount e, the diameter d and the length L2 of the small shaft portion 14 can be freely set as far as the turbine side portion corresponding to the body portion B of the secondary vibration mode of bending can be held at approximately the same diameter as the bearing portion.
In this case, specifically, it is preferable to set the offset amount e, the diameter d and the length L2 in accordance with a computer simulation in such a manner that the primary critical speed is lowered with respect to a predetermined rated speed, and a decreasing amount (or rate) of the secondary critical speed does not exceed a decreasing amount (or rate) of the primary critical speed.
In accordance with the structure of the present invention mentioned above, since the small shaft portion 14 having the smaller diameter than the bearing portion is provided between the bearings, it is possible to reduce the vibration and the noise by decreasing the primary critical speed of bending.
Further, since the small shaft portion 14 is offset to the compressor side and the turbine side portion corresponding to the body portion B1 of the secondary vibration mode of bending has approximately the same diameter as the bearing portion, a rigidity of the shaft positioned in the body portion of the secondary vibration mode of bending is not lowered, so that it is possible to suppress the decreasing of the secondary critical speed of bending to the minimum so as to increase a stability of the shaft system and improve a reliability.
In this case, the turbine side portion corresponding to the body portion B1 of the secondary vibration mode of bending may be made bigger than the small shaft portion 14 and smaller than the bearing portion, within a range capable of suppressing the decreasing of the secondary critical speed of bending. Further, the portion may be made bigger than the small shaft portion 14 and the bearing portion.
From the drawing, there can be known that it is possible to decrease the primary critical speed, however, the secondary critical speed is decreased at the same time, in the case (B) that the small shaft length is maximum (L1), in comparison with the case (A) that the small shaft portion 14 is not provided, so that the secondary critical speed comes close to the rated speed, and the shaft system becomes unstable.
Further, in the case that the small shaft length is intermediate (L2), there can be known that the case (D) that the offset is provided has a lower rate (about 5%) of decreasing of the secondary critical speed than a rate (about 15%) of decreasing of the primary critical speed, in comparison with the case (C) that the offset is not provided, and it is possible to decrease the primary critical speed while suppressing the decreasing of the secondary critical speed.
In this case, this embodiment shows the case that the maximum (L1) of the small shaft length is about 24 mm, and the intermediate (L2) of the small shaft length is about 12 mm, however, the present invention is not limited to this, but it is preferable to set optimum offset amount e, diameter d and length L2 with respect to a predetermined rated speed in accordance with a computer simulation.
In this case, it goes without saying that the present invention is not limited to the embodiment mentioned above, but can be variously modified within the range of the scope of the present invention.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US2588459 *||Mar 20, 1948||Mar 11, 1952||Roulements A Billes Miniatures||High-speed spindle|
|US2918207 *||Dec 16, 1957||Dec 22, 1959||Gen Motors Corp||Turbocharger|
|US3612628 *||Jan 22, 1969||Oct 12, 1971||Lucas Industries Ltd||Gas bearings|
|US3632222 *||Oct 21, 1970||Jan 4, 1972||Avco Corp||Damping means for differential gas turbine engine|
|US3675056||Jan 4, 1971||Jul 4, 1972||Gen Electric||Hermetically sealed dynamoelectric machine|
|US3728857 *||Jun 22, 1971||Apr 24, 1973||Gates Rubber Co||Turbo-compressor-pump|
|US3742123||Nov 25, 1970||Jun 26, 1973||Haub L||Insulator for electric wires|
|US3778194||Aug 28, 1972||Dec 11, 1973||Carrier Corp||Turbocharger structure|
|US3811741 *||Dec 26, 1972||May 21, 1974||Garrett Corp||Bearing|
|US3890780 *||Aug 31, 1973||Jun 24, 1975||Mtu Muenchen Gmbh||Bearing support for thermal power engines|
|US3927530||May 28, 1974||Dec 23, 1975||Anton Braun||Supercharged internal combustion engine|
|US3961867||Mar 27, 1974||Jun 8, 1976||Holset Engineering Company Limited||Rotatable assembly with rotor abraded by seal ring|
|US4061279 *||Feb 4, 1977||Dec 6, 1977||Pennsylvania Crusher Corporation||High-speed rotating crushing machinery|
|US4198063||Jul 14, 1978||Apr 15, 1980||Ishikawajima-Harima Jukogyo Kabushiki Kaisha||Shaft sealing device for turbocharger|
|US4253031||May 22, 1979||Feb 24, 1981||Robert Bosch Gmbh||Directly driven dynamo electric machine-gas turbine generator structure|
|US4301375||Jan 2, 1980||Nov 17, 1981||Sea Solar Power, Inc.||Turbo-generator unit and system|
|US4641977||Mar 21, 1984||Feb 10, 1987||Woollenweber William E||Bearing system|
|US4704075||Jan 24, 1986||Nov 3, 1987||Johnston Andrew E||Turbocharger water-cooled bearing housing|
|US4745755||Jul 23, 1986||May 24, 1988||Isuzu Motors Limited||Control system for supercharged internal combustion engine|
|US4757686||Aug 29, 1986||Jul 19, 1988||Isuzu Motors Limited||Control system for supercharger in internal combustion engine|
|US4833887||Aug 28, 1986||May 30, 1989||Isuzu Motors Limited||Auxiliary apparatus for a turbocharged internal combustion engine|
|US4872817 *||Jul 19, 1984||Oct 10, 1989||Allied-Signal Inc.||Integral deflection washer compressor wheel|
|US4883370 *||Jan 27, 1987||Nov 28, 1989||C.S.U. Ltd.||Rotary structure|
|US5121605||Mar 12, 1990||Jun 16, 1992||Hitachi, Ltd||Turbo-charger with rotary machine|
|US5243880 *||Mar 27, 1991||Sep 14, 1993||Gkn Automotive Ag||Driveshaft|
|US5323613||Mar 30, 1993||Jun 28, 1994||Isuzu Motors Limited||Motor-generator voltage controller for turbocharger|
|US5587332||Sep 1, 1992||Dec 24, 1996||Vlsi Technology, Inc.||Method of making flash memory cell|
|US5605045||Sep 18, 1995||Feb 25, 1997||Turbodyne Systems, Inc.||Turbocharging system with integral assisting electric motor and cooling system therefor|
|US5798587||Jan 22, 1997||Aug 25, 1998||Industrial Technology Research Institute||Cooling loop structure of high speed spindle|
|US5834117||Nov 12, 1996||Nov 10, 1998||Sumitomo Wiring Systems, Ltd.||Heat-resistant electrical wire comprising a benzimidazole-based polymer coating|
|US5857332||Dec 20, 1996||Jan 12, 1999||Turbodyne Systems, Inc.||Bearing systems for motor-assisted turbochargers for internal combustion engines|
|US5870894||Jul 16, 1996||Feb 16, 1999||Turbodyne Systems, Inc.||Motor-assisted supercharging devices for internal combustion engines|
|US5904471||Dec 20, 1996||May 18, 1999||Turbodyne Systems, Inc.||Cooling means for a motor-driven centrifugal air compressor|
|US5906098||Oct 15, 1996||May 25, 1999||Turbodyne Systems, Inc.||Motor-generator assisted turbocharging systems for use with internal combustion engines and control method therefor|
|US6032466||May 14, 1997||Mar 7, 2000||Turbodyne Systems, Inc.||Motor-assisted turbochargers for internal combustion engines|
|US6102672||Sep 10, 1997||Aug 15, 2000||Turbodyne Systems, Inc.||Motor-driven centrifugal air compressor with internal cooling airflow|
|US6129524||Dec 7, 1998||Oct 10, 2000||Turbodyne Systems, Inc.||Motor-driven centrifugal air compressor with axial airflow|
|US6145314||Sep 14, 1998||Nov 14, 2000||Turbodyne Systems, Inc.||Compressor wheels and magnet assemblies for internal combustion engine supercharging devices|
|US6160332||Jul 8, 1999||Dec 12, 2000||Mitsubishi Denki Kabushiki Kaisha||Liquid cooled brushless generator for vehicles|
|US6218747||Sep 1, 1999||Apr 17, 2001||Mitsubishi Denki Kabushiki Kaisha||Car AC generator|
|US6253747 *||Feb 25, 2000||Jul 3, 2001||Eaton Corporation||Torsional coupling for supercharger|
|US6257834||Sep 24, 1999||Jul 10, 2001||Asea Brown Boveri Ag||Method and arrangement for the indirect cooling of the flow in radial gaps formed between rotors and stators of turbomachines|
|US6278199||Feb 23, 2000||Aug 21, 2001||International Rectifier Corp.||Electronic single switch module|
|US6293769||Feb 1, 2000||Sep 25, 2001||Pierburg Ag||Canned pump with dry rotor compartment|
|US6416281||Sep 24, 1999||Jul 9, 2002||Asea Brown Boveri Ag||Method and arrangement for cooling the flow in radial gaps formed between rotors and stators of turbomachines|
|US6449950||Sep 12, 2000||Sep 17, 2002||Honeywell International Inc.||Rotor and bearing system for electrically assisted turbocharger|
|US6609375||Sep 14, 2001||Aug 26, 2003||Honeywell International Inc.||Air cooling system for electric assisted turbocharger|
|US6647724||Jul 30, 2002||Nov 18, 2003||Honeywell International Inc.||Electric boost and/or generator|
|US6668553||Sep 13, 2002||Dec 30, 2003||Honeywell International Inc.||Ejector-based cooling system for turbochargers|
|US6753628||Dec 22, 1999||Jun 22, 2004||Encap Motor Corporation||High speed spindle motor for disc drive|
|US6768332||Mar 12, 2003||Jul 27, 2004||Advanced Semiconductor Engineering Inc.||Semiconductor wafer and testing method for the same|
|US6845617||Dec 20, 2003||Jan 25, 2005||Honeywell International Inc||Center housing design for electric assisted turbocharger|
|US6871499||Dec 20, 2003||Mar 29, 2005||Honeywell Interntional, Inc.||Oil pressure detector for electric assisted turbocharger|
|US6986648||May 2, 2003||Jan 17, 2006||Dana Automotive Limited||Electric pump|
|US7008194||Sep 2, 2003||Mar 7, 2006||Borgwarner Inc.||Turbocharger|
|US7010916||Jun 4, 2004||Mar 14, 2006||Daimlechrysler Ag||Exhaust-gas turbocharger|
|US7056103||Mar 5, 2004||Jun 6, 2006||Honeywell International, Inc.||Method and apparatus for cooling turbomachinery components|
|US7352077||Aug 8, 2006||Apr 1, 2008||Ishikawajima-Harima Heavy Industries Co., Ltd.||Motor-driven supercharger|
|US7360361||Apr 7, 2006||Apr 22, 2008||Advanced Propulsion Technologies, Inc.||Turbocharger|
|US7458214||Apr 15, 2003||Dec 2, 2008||Honeywell International, Inc.||Electric motor cartridge for an electrically assisted turbocharger|
|US7670056 *||Mar 22, 2007||Mar 2, 2010||Honeywell International Inc.||Stepped outer diameter semi-floating bearing|
|US7753591 *||Jul 13, 2010||Honeywell International Inc.||Turbocharger bearing and associated components|
|US7765846 *||Aug 3, 2010||Neumayer Tekfor Holding Gmbh||Method of producing a hollow shaft|
|US20030017879 *||Jul 9, 2002||Jan 23, 2003||Chun-Yi Tsay||Automatic stabilizer for high-speed drill spindle|
|US20030051475||Sep 14, 2001||Mar 20, 2003||John Allen||Air cooling system for electric assisted turbocharger|
|US20030118461||Jan 24, 2001||Jun 26, 2003||Josef Hodapp||Radial turbo-blower|
|US20040229703 *||May 13, 2003||Nov 18, 2004||Jackson Robert N.||Sealed axially displaceable slip joint|
|US20050082941||Oct 6, 2004||Apr 21, 2005||Toyota Jidosha Kabushiki Kaisha||Turbocharger with rotating electric machine|
|US20060081226||Jun 11, 2003||Apr 20, 2006||Martin-Peter Bolz||Electrical charge air compressor provided with an integrated air cooling system|
|US20060123783||Apr 15, 2003||Jun 15, 2006||Noelle Philippe||Electric motor cartridge for an electrically assisted turbocharger|
|US20060225419||Apr 7, 2006||Oct 12, 2006||Applied Technologies, Inc.||Turbocharger|
|US20060245913||Mar 27, 2006||Nov 2, 2006||Abb Research Ltd.||Compressor cleaning system|
|US20070036664||Aug 10, 2006||Feb 15, 2007||Ishikawajima-Harima Heavy Industries Co., Ltd.||Supercharger with electric motor|
|US20070108772||Aug 8, 2006||May 17, 2007||Ishikawajima-Harima Heavy Industries Co., Ltd.||Motor-driven supercharger|
|US20080087018||Oct 11, 2006||Apr 17, 2008||Woollenweber William E||Bearing systems for high-speed rotating machinery|
|US20090025386||Oct 12, 2004||Jan 29, 2009||Peer Rumsby||Electrically assisted turbocharger|
|US20100132358 *||Feb 1, 2010||Jun 3, 2010||Purdey Matthew J||Turbocharger bearing assembly and lubrication thereof|
|US20100175377||Apr 2, 2009||Jul 15, 2010||Will Hippen||Cooling an electrically controlled turbocharger|
|US20100266430||May 26, 2008||Oct 21, 2010||Ihi Corporation||Turbocharger with electric motor|
|US20110124421 *||Dec 2, 2004||May 26, 2011||Christine Kienhofer||Method for producing a tubular drive shaft, in particular a cardan shaft for a motor vehicle|
|CA2068369A1||May 11, 1992||Nov 11, 1992||Bernhard Wuest||Electrical machine|
|CH266731A||Title not available|
|CN2605696Y||Mar 19, 2003||Mar 3, 2004||哈尔滨工业大学新型热能有限责任公司||Liquid-flow thermal energy generator for enclosed water-cooled motor|
|DE4115273C1||May 10, 1991||Jun 4, 1992||J.M. Voith Gmbh, 7920 Heidenheim, De||Title not available|
|DE10022113A1||May 6, 2000||Nov 15, 2001||Daimler Chrysler Ag||Motor vehicle hybrid drive has controller that regulates charging pressure depending on operating conditions, limits charging pressure by regulating electrical power of electrical machine|
|DE10156704A1||Nov 13, 2001||May 22, 2003||Iav Gmbh||Method and appliance for operating exhaust gas turbocharger for IC engines with electrically assisted drive based on comparison of actual operating conditions and family of operating characteristics|
|DE102005052363A1||Nov 2, 2005||May 3, 2007||Siemens Ag||Electric motor for actuation of camshaft in motor vehicle, has cup-shaped outer cover arranged around sleeve that is washed with cooling medium, where cover has cooling medium inlet and cooling medium outlet|
|EP0079100A1||Nov 1, 1982||May 18, 1983||Microturbo S.A.||Turbo charger for a combustion engine|
|EP0212988A2||Aug 28, 1986||Mar 4, 1987||Isuzu Motors Limited||Apparatus for controlling a turbocharger of an internal combustion engine|
|EP0304259A1||Aug 15, 1988||Feb 22, 1989||Isuzu Motors Limited||Turbocharger|
|EP1348848A2||Mar 25, 2003||Oct 1, 2003||Toyota Jidosha Kabushiki Kaisha||Turbocharger|
|FR2859499A1||Title not available|
|GB2021874A||Title not available|
|GB2162377A||Title not available|
|JP3389748B2||Title not available|
|JP61237830A||Title not available|
|JP2000110557A||Title not available|
|JP2000130176A||Title not available|
|JP2000145468A||Title not available|
|JP2000514987A||Title not available|
|JP2001295655A||Title not available|
|JP2001527613A||Title not available|
|JP2003232340A||Title not available|
|JP2005207337A||Title not available|
|JP2005248799A||Title not available|
|JP2007297973A||Title not available|
|JP2007321698A||Title not available|
|JP2007321699A||Title not available|
|JP2009243361A||Title not available|
|JP2009243365A||Title not available|
|JP2010121589A||Title not available|
|JPH0299722A||Title not available|
|JPH0526202A||Title not available|
|JPH0642361A||Title not available|
|JPH01171006A||Title not available|
|JPH03138430A||Title not available|
|JPH04119624A||Title not available|
|JPH05199708A||Title not available|
|JPH06288242A||Title not available|
|JPH06346748A||Title not available|
|JPH07102988A||Title not available|
|JPH10299500A||Title not available|
|JPH11182259A||Title not available|
|JPS6149126A||Title not available|
|JPS6419122A||Title not available|
|JPS58124024A||Title not available|
|JPS60153826A||Title not available|
|JPS61237830A||Title not available|
|KR1020040105849A||Title not available|
|WO2005024202A1||Sep 5, 2003||Mar 17, 2005||Honeywell International Inc.||Electric power connection for electrically assisted turbocharger|
|WO2005028876A1||Sep 22, 2004||Mar 31, 2005||Abb Research Ltd.||Compressor cleaning system|
|WO2005113961A1||May 18, 2005||Dec 1, 2005||Toyota Jidosha Kabushiki Kaisha||Motor-assisted turbo charger for an internal combustion engine|
|1||Chinese Office Action issued in co-pending U.S. Appl. No. 12/377,987. Chinese Patent Application No. 200780030544.0. mailed Mar. 8, 2010.|
|2||Espacenet English Abstract corresponding to the Hwang Document KR20040089337, filed in a related application as "Exhibit B".|
|3||First Office Action, issued in corresponding Chinese Patent Application No. 200780020456.2, issued Nov. 20, 2009.|
|4||http://answers.yahoo.com/question/index?qid=20100220052035A, dated Feb. 20, 2010, downloaded Mar. 9, 2011, 1 page.|
|5||http://encyclopedia2.thefreedictionary.com/friction+fit, downloaded Mar. 9, 2011, 2 pgs.|
|6||http://www.answers.com/topic/friction-fit, downloaded Mar. 9, 2011, 1 page.|
|7||http://www.roymech.co.uk/Useful-Tables/ISO-Tolerances/ISO, downloaded Mar. 9, 2011, 2 pgs.|
|8||http://www.roymech.co.uk/Useful—Tables/ISO—Tolerances/ISO, downloaded Mar. 9, 2011, 2 pgs.|
|9||International Search Report issued in corresponding application No. PCT/JP2007/051607, completed Feb. 15, 2007 and mailed Feb. 27, 2007.|
|10||Machine English Translation of the Hwang Document KR20040089337, obtained from the Korean Patent Office, filed in a related application as "Exhibit C,".|
|11||Machine translation of JP2000-145468, Published on May 26, 2000.|
|12||Microfilm of the specification and drawings annexed to the request of Japanese Utility Model Application No. 10710/1983 (Laid-Open No. 116537/1984), Toyota Motor Corp, Aug. 6, 1984.|
|13||Microfilm of the specification and drawings annexed to the request of Japanese Utility Model Application No. 115203/1986 (Laid-Open No. 22301/1988), Nissan Motor Corp, Feb. 15, 1988.|
|14||Microfilm of the specification and drawings annexed to the request of Japanese Utility Model Application No. 134167/1984 (Laid-open No. 49126/1986), dated Apr. 2, 1986.|
|15||Microfilm of the specification and drawings annexed to the request of Japanese Utility Model Application No. 142414/1985 (Laid-Open No. 49629/1987), Nissan Motor Corp, Mar. 27, 1987.|
|16||Notice of Allowance issued in co-pending U.S. Appl. No. 12/300,746, dated Apr. 19, 2011.|
|17||Office Action dated Nov. 1, 2011 in corresponding Japanese Patent Application No. 10-2008-7021399.|
|18||Office Action dated Oct. 11, 2011 in corresponding Korean Patent Application No. 10-2009-7002938.|
|19||Office Action dated Oct. 11, 2011 in corresponding Korean Patent Application No. 10-2009-7002939.|
|20||Office Action issued Feb. 22, 2010 in co-pending U.S. Appl. No. 11/617,211.|
|21||Office Action issued in co-pending U.S. Appl. No. 12/300,726, dated Dec. 21, 2010.|
|22||Office Action issued in co-pending U.S. Appl. No. 12/300,726, dated May 2, 2011.|
|23||Office Action issued in co-pending U.S. Appl. No. 12/300,746, dated Dec. 22, 2010.|
|24||Office Action issued in Japanese Patent Application No. 2006-207973, of co-pending U.S. Appl. No. 12/864,837, dated Jan. 11, 2011 with an english translation.|
|25||Office Action issued in Korean Patent Application No. 10-2008-7028778, dated Feb. 28, 2011, of co-pending U.S. Appl. No. 12/300,726 and its english translation.|
|26||Office Action issued in related Korean Patent Application No. 10-2007-0005555 (included herein in Korean and Japanese) dated Mar. 30, 2009.|
|27||Office Action mailed Jul. 12, 2011 in co-pending U.S. Appl. No. 12/377,987.|
|28||Office Action mailed Jul. 7, 2011 in co-pending U.S. Appl. No. 12/377,977.|
|29||Patent Abstracts of Japan English Abstract corresponding to the Hattori Document JP61-237830, a filed in a related application as "Exhibit A".|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US9404534 *||Nov 30, 2012||Aug 2, 2016||Honeywell International Inc.||Rotating assemblies of turbomachinery, foil journal bearing assemblies thereof, and methods for producing journals of the foil journal bearing assemblies|
|US20140154058 *||Nov 30, 2012||Jun 5, 2014||Honeywell International Inc.||Rotating assemblies of turbomachinery, foil journal bearing assemblies thereof, and methods for producing journals of the foil journal bearing assemblies|
|U.S. Classification||417/407, 464/180, 464/162, 464/183|
|International Classification||F16C3/03, F04B35/00, F04B17/00, F16C3/00|
|Cooperative Classification||Y10T464/50, F05D2250/293, F05D2250/291, F05D2260/96, F05D2220/40, F16C2360/24, F01D25/166, F16C3/02, F01D5/048, F01D25/04, F05D2240/53|
|European Classification||F01D25/16C, F01D5/04, F16C3/02|
|Aug 27, 2008||AS||Assignment|
Owner name: IHI CORPORATION, JAPAN
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SHIMIZU, MASAHIRO;REEL/FRAME:021447/0171
Effective date: 20080714
|Sep 30, 2015||FPAY||Fee payment|
Year of fee payment: 4